Tuned mass damper

ABSTRACT

A tuned mass damper comprises a mass ( 1 ) restrained to a structure ( 2 ) through supporting means ( 3 ) suitable to allow a pendulum motion of said mass ( 1 ) when said structure ( 2 ) is subject to an external force, as well as damping means suitable for absorbing a portion of the kinetic energy of the moving mass ( 1 ). The supporting means ( 3 ) comprise at least one bearing ( 3 ) provided with a concave cylindrical sliding surface ( 3   a ) and the damping means are made as a coating of a controlled friction material of said sliding surface ( 3   a ).

The present invention relates to a tuned mass damper and particularly to a tuned mass damper suitable for the application to civil and building structures (civil structures and buildings) like skyscrapers, towers and bridges.

Tuned mass dampers, also know under the acronym TMD, are devices for damping vibrations used for stabilizing the motion of a structure subject to an external force, thus preventing the structure from being damaged or even yielding.

Such devices are essentially mechanical systems of the mass-spring-damper type provided with one or more degrees of freedom and designed to be in resonance with the structure in which they are installed. Whenever the structure vibrates subject to any force like, for example, wind or an earthquake, the dampers oppose the inertia of the mass to the vibration motion, thus generating, as an effect of the resonance, equal and opposed forces capable of nullifying the motions of the structure.

In the field of building and construction, and particularly in the construction of very tall structures like skyscrapers, towers and bridges that are very sensitive to wind and seismic events, tuned mass dampers are made as pendulum structures wherein the mass is a cement or steel block supported by ropes or arms restrained to the structure. The mass moves according to the law of motion of a pendulum, storing and releasing potential energy similarly to a mass restrained by a spring of a mass-spring-damper system, while the damping action is accomplished by one or more damping means, e.g. of a hydraulic type, arranged in the one or more preset directions of motion.

Tuned mass dampers of the pendulum type have remarkable installation problems, due to the size of both the suspended masses and the related supporting means. For instance, in the case of a skyscraper the structure of a tuned mass damper may occupy even some floors of the building in height.

Moreover, after the installation, a tuned mass damper always requires a “tuning” step with respect to the real dynamic behavior of the structure. In fact, a damper is designed on the basis of a theoretical model of the structure to which it will be applied, therefore adjustments of the fundamental period are always required once the structure has been completed. Generally, a tuning step is rather complicated and expensive since the adjustment of the length of the ropes or arms supporting the mass requires the use of equipment like winches or tension rods, which may be removably or even permanently installed.

It is therefore an object of the present invention to provide a tuned mass damper capable of overcoming said disadvantages. Said object is achieved by means of a tuned mass damper whose main features are disclosed in the first claim, while other features are disclosed in the remaining claims.

The tuned mass damper according to the present invention comprises at least one mass restrained to supporting means suitable to allow a pendulum motion thereof when the structure is subject to an external force. The supporting means comprise at least one bearing provided with a concave cylindrical sliding surface.

The main advantage of the tuned mass damper according to the present invention is that it has a remarkably smaller size with respect to known dampers, thus allowing an easier installation into the structure for which it is intended. In fact, choosing mass supporting means in the form of at least one concave cylindrical bearing allows to reduce the system size, which substantially coincides with the mass size only. Consequently, it is possible to reduce both the manufacturing and installation costs of the damper.

Moreover, by coating or making the sliding surfaces of the bearings with controlled friction materials, it is possible to accomplish damping means without resorting to traditional external devices, e.g. of a hydraulic type or the like, installed on the structure and restrained to the mass, thus further reducing the manufacturing costs.

Another advantage offered by the invention is that the tuning step of the damper is strongly simplified. In fact, the sliding surfaces of the bearings are provided with variable curvature radiuses, thus allowing to adjust the fundamental period by simply varying the contact point between the supporting means and the mass transversally to its direction of motion.

Still another advantage offered by the invention is that it is possible to make a damper provided with more degrees of freedom by arranging the bearings on a multilayer structure and orienting the sliding surfaces of the bearings of each layer such as to define more directions of motion.

Moreover, the behavior of the damper in the various directions of motion may be differentiated by choosing different curvatures of the sliding surfaces and/or using different controlled friction materials.

Further advantages and features of the tuned mass damper according to the present invention will become clear to those skilled in the art from the following detailed and non-limiting description of some embodiments thereof with reference to the attached drawings, wherein:

FIG. 1 shows a perspective view of a first embodiment of a tuned mass damper according to the present invention;

FIG. 2 shows a detail H of FIG. 1;

FIG. 3 shows a perspective view of a second embodiment of a tuned mass damper according to the present invention, provided with means for tuning the fundamental period;

FIG. 4 shows a detail IV of FIG. 3;

FIG. 5 shows a cross-section V-V of FIG. 3;

FIGS. 6 and 7 show a detail VI and a detail VII of FIG. 5, respectively;

FIG. 8 shows a perspective view of a third embodiment of a tuned mass damper according to the present invention, provided with two degrees of freedom;

FIG. 9 shows a detail IX of FIG. 8;

FIG. 10 shows a cross-section X-X of FIG. 8; and

FIG. 11 shows a detail XI of FIG. 10.

Referring to FIGS. 1 and 2, the tuned mass damper according to the present invention comprises in a known way a mass 1 restrained to a structure 2 through supporting means 3 suitable to allow a pendulum motion of mass 1 when structure 2 is subject to an external force as, for instance, wind or an earthquake.

According to the inventive concept which is the basis of the present invention, the supporting means 3 comprise at least one bearing provided with a concave cylindrical sliding surface 3 a. Mass 1, made to move upon the action of a force acting on the structure, moves along the sliding surface 3 a of bearing 3, increasing and decreasing its potential energy according to the law of motion of a pendulum. The fundamental period of the oscillation of mass 1, defined by the radius of the sliding surface 3 a, is substantially equal to the fundamental period of structure 2, thus the damper and structure 2 are resonant.

In the design of the damper according to the present invention, mass 1 is so dimensioned as to be equal to 2-4% of the total mass of the structure to which it is applied.

Moreover, the size of mass 1 is remarkably larger with respect to the order of magnitude of the movements that mass 1 makes in order to react against the movements of structure 2. Therefore, both for encumbrance and stability reasons the supporting means comprise a plurality of bearings, whose concave cylindrical sliding surfaces 3 a have the same curvature and are arranged parallel to each other, thus defining one single direction of motion for mass 1. Correspondingly, mass 1 is provided with a plurality of feet 4 arranged at positions corresponding to the positions of bearings 3.

In the embodiment shown in FIG. 1, for example, the damper comprises four bearings 3 respectively provided with sliding surfaces 3 a and mass 1 is provided with four feet 4 arranged at positions corresponding to the positions of bearings 3.

As shown in the detail of FIG. 2, each foot 4 consists of an upper portion 4 a restrained to mass 1 and of a lower portion 4 b that has a convex cylindrical surface 4 c suitable to contact the sliding surface 3 a of the respective bearing 3.

The upper portion 4 a and the lower portion 4 b of each foot 4 are movable with respect to each other and coupled by means of a cylindrical or spherical cap joint allowing a relative rotation thereof. In this way, mass 1 moves along the sliding surfaces 3 a of bearings 3 without rotating with respect to the plane of structure 2.

During the motion of mass 1, a certain amount of kinetic energy is dissipated through friction in the contact between the concave cylindrical sliding surfaces 3 a of bearings 3 and the convex cylindrical surfaces 4 c of feet 4, thus achieving a damping effect. Therefore, without resorting to external damping devices as in known applications, the damper according to the present invention may be provided with damping means in the form of coatings of controlled friction materials of the concave cylindrical sliding surfaces 3 a of bearings 3 and the convex cylindrical surfaces 4 c of feet 4.

Alternatively, bearings 3 and the lower portions 4 b of feet 4 may be entirely made of controlled friction materials.

Preferably, the controlled friction materials are combined with each other so as to minimize the wear. Suitable controlled friction materials are, for example, stainless steel and polymeric materials selected among, e.g., polyethylene, polyamidic resins and PTFE suitably modified and/or filled.

Referring to FIGS. 3-7, a second embodiment of the damper according to the invention is now described, wherein in order to allow the tuning of the damper with respect to a structure 2, the sliding surfaces 3 a of bearings 3 have radiuses of curvature transversally varying with respect to the direction of motion of mass 1, and the damper comprises driving means 6 suitable for modifying the contact points between mass 1 and the sliding surfaces 3 a. By modifying the contact points between the sliding surface 3 a and mass 1, the latter will move following a path having a different radius, thus allowing to vary the fundamental period and thereby to tune the damper according to the actual fundamental period of structure 2. Preferably, the driving means 6 do not act directly on mass 1, which is very cumbersome and difficult to move, but on its feet 4 by modifying their relative distance.

The bearings 3 are arranged in pairs on structure 2 with the respective sliding surfaces 3 a parallel to each other and having a curvature radius increasing outwards when starting from the plane of symmetry of the damper in which mass 1 moves. The feet 4 are correspondingly assembled in pairs and movably on guides 5 fixed to mass 1 and transversally arranged with respect to its direction of motion, and are connected to each other through the driving means 6.

The driving means 6 comprise a worm provided at one end with a maneuvering member 7, e.g. a lever, suitable to allow the rotation thereof around its axis. The worm 6 comprises a first threaded portion 6 a, inserted in a threaded hole formed in the upper portion 4 a of a first foot 4 of the pair, and a second portion 6 b with opposite threading inserted in a threaded hole formed in the upper portion 4 a of a second foot 4 of the pair. By rotating lever 7 clockwise or counterclockwise, the rotation of the worm causes feet 4 to come close to each other or to move away along guide 5, thus varying their relative distance. In this way, feet 4 move to portions of the sliding surfaces 3 a having a different radius, thus resulting in a variation of the fundamental period of the damper.

The curvature of the concave cylindrical surfaces 3 a of bearings 3 may vary continuously or discretely, with more or less marked changes in curvature between one portion of the sliding surface 3 a and another in order to obtain a larger or smaller tuning range with the same size of the sliding surface 3 a.

The tuned mass damper according to the present invention may have more degrees of freedom, thus being able to be employed also when more directions of motion are foreseen, e.g. two mutually perpendicular directions.

FIGS. 8-11 show a third embodiment of the damper according to the present invention, wherein mass 1 is supported by a first series of feet 4 contacting a first series of bearings 3. The first series of bearings 3 is restrained to a base 8 and the sliding surfaces of bearings 3 are so oriented as to define a first direction of motion marked by an arrow L. On the side of base 8 opposite the first series of bearings 3, a second series of bearings 3′ is provided, which contact a second series of feet 4′ restrained to structure 2 through corresponding guides 5′ along which they are adjustable through related driving means 6′. The sliding surfaces 3 a′ of the bearings 3′ of the second series are so oriented as to define a second direction of motion, which is perpendicular to the first one and marked by an arrow T.

Therefore, in this case the damper is provided with two degrees of freedom in the two directions of motion defined by the two series of bearings 3, 3′.

Other directions of motion may be similarly provided by arranging the bearings in a multilayer structure wherein each layer comprises a base and one or more bearings as well as a series of feet arranged at positions corresponding to the positions of the bearings. For each layer the direction of motion is defined by the orientation of the sliding surfaces of the one or more bearings arranged thereon.

In the case of a multilayer structure, the total mass of the damper comprises not only mass 1 but also the masses of the distinct bases 8, which are selectively activated depending on the directions of motion simultaneously applied by an external force.

As in the above-described embodiment provided with one degree of freedom, in order to allow the tuning of the fundamental period of the damper, the sliding surfaces 3 a, 3 a′ of bearings 3, 3′ have curvature radiuses transversally varying with respect to the direction of motion defined by them and each layer comprises driving means 6, 6′ suitable for modifying the contact points between feet 4, 4′ and the sliding surfaces 3 a, 3 a′.

Moreover, it is possible to differentiate the damping characteristics in the various directions of motion by using in the various layers different controlled friction materials for the couplings between the concave cylindrical sliding surfaces 3 a, 3 a′ of bearings 3, 3′ and the convex cylindrical surfaces 4 c, 4 c′ of feet 4, 4′, thus obtaining many possibilities for optimizing the response of the damper.

It is clear that the above-described and illustrated embodiments of the tuned mass damper are only examples susceptible of numerous variations. In particular, it is possible to use other controlled friction materials well known to those skilled in the art for coating the sliding surfaces. In addition, for the sliding surfaces made of a metal material it is possible to use special materials like chrome-nickel steel in order to provide high characteristics of hardness and minimize the wear. 

1-14. (canceled)
 15. A tuned mass damper comprising at least one mass and supporting means restraining said mass to a structure and suitable to allow a pendulum motion thereof when said structure is subject to an external force, said tuned mass damper further comprising damping means suitable for absorbing a portion of the kinetic energy of the mass when in motion, wherein said supporting means comprise at least one bearing and wherein said bearing is provided with a concave cylindrical sliding surface.
 16. The damper of claim 15, wherein said supporting means comprise a plurality of bearings having concave cylindrical sliding surfaces of equal curvature and arranged parallel to each other, and wherein said mass is provided with a plurality of feet arranged at positions corresponding to the positions of the bearings.
 17. The damper of claim 16, wherein each foot consists of an upper portion restrained to the mass and of a lower portion that has a convex cylindrical surface suitable to contact the concave cylindrical sliding surface of the respective bearing.
 18. The damper of claim 17, wherein each foot comprises a cylindrical or spherical cap joint coupling said upper portion to said lower portion of each foot and wherein said cylindrical or spherical cap joint is suitable to allow a relative movement and a relative rotation between the upper portion and the lower portion of each foot.
 19. The damper of claim 17, wherein the damping means are made as coatings of controlled friction materials of the concave cylindrical sliding surfaces of the bearings and of the convex cylindrical surfaces of the lower portions of the feet.
 20. The damper of claim 19, wherein the bearings and the lower portions of the feet are entirely made of controlled friction materials.
 21. The damper of claim 19, wherein said controlled friction materials are stainless steel and polymeric materials selected the group consisting of polyethylene, polyamidic resins and PTFE modified and/or filled.
 22. The damper of claim 20, wherein said controlled friction materials are stainless steel and polymeric materials selected the group consisting of polyethylene, polyamidic resins and PTFE modified and/or filled.
 23. The damper of claim 16, wherein the sliding surfaces of the bearings have curvature radiuses transversally varying with respect to the direction of motion of the mass, and wherein the damper further comprises driving means suitable for modifying the contact points between the mass and said sliding surfaces.
 24. The damper of claim 23, wherein the bearings are arranged in pairs on the structure, the respective sliding surfaces being parallel to each other and having a curvature radius increasing outwards when starting from the plane of symmetry of the damper in which the mass moves, the feet being correspondingly mounted in pairs and movably on guides fixed to the mass and arranged transversally to its motion direction, and wherein said driving means are connected to each pair of feet and are suitable for modifying their relative distance.
 25. The damper of claim 24, wherein said driving means comprises a worm, said worm being provided at one end with a maneuvering member suitable to allow the rotation thereof around its axis, the worm having a first threaded portion inserted in a threaded hole formed in the upper portion of a first foot of the pair and a second portion with opposite threading inserted in a threaded hole formed in the upper portion of a second foot of the pair.
 26. The damper of claim 16, wherein the bearings are arranged in a multilayer structure, each layer comprising at least a base and one or more bearings as well as a series of feet at positions corresponding to the positions of the bearings, the direction of motion for each layer being defined by the orientation of the sliding surfaces of the one or more bearings arranged thereon.
 27. The damper of claim 26, wherein for each layer of said multilayer structure the sliding surfaces of the bearings have curvature radiuses transversally varying with respect to the direction of motion defined by them, and wherein each layer further comprises driving means suitable for modifying the contact points between the feet and the sliding surfaces.
 28. The damper of claim 26, wherein in the various layers of said multilayer structure the couplings between the concave cylindrical sliding surfaces of the bearings and the convex cylindrical surfaces of the feet are made with different controlled friction materials.
 29. The damper of claim 27, wherein in the various layers of said multilayer structure the couplings between the concave cylindrical sliding surfaces of the bearings and the convex cylindrical surfaces of the feet are made with different controlled friction materials.
 30. The damper of claim 15, wherein the mass is equal to 2-4% of the total mass of the structure.
 31. The damper of claim 18, wherein the damping means are made as coatings of controlled friction materials of the concave cylindrical sliding surfaces of the bearings and of the convex cylindrical surfaces of the lower portions of the feet. 